WO1997015800A1 - Systeme de transport de chaleur - Google Patents

Systeme de transport de chaleur Download PDF

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Publication number
WO1997015800A1
WO1997015800A1 PCT/JP1996/003130 JP9603130W WO9715800A1 WO 1997015800 A1 WO1997015800 A1 WO 1997015800A1 JP 9603130 W JP9603130 W JP 9603130W WO 9715800 A1 WO9715800 A1 WO 9715800A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
refrigerant
heat exchange
heat source
heat exchanger
Prior art date
Application number
PCT/JP1996/003130
Other languages
English (en)
Japanese (ja)
Inventor
Shinri Sada
Yasushi Hori
Osamu Tanaka
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP96935453A priority Critical patent/EP0857937B1/fr
Priority to DE69618474T priority patent/DE69618474T2/de
Priority to AU73369/96A priority patent/AU717801B2/en
Priority to US09/051,484 priority patent/US5943879A/en
Publication of WO1997015800A1 publication Critical patent/WO1997015800A1/fr
Priority to HK99102449A priority patent/HK1017423A1/xx

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0003—Exclusively-fluid systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • the present invention relates to a heat transfer device, for example, a heat transfer device that can be used as a refrigerant circuit of an air conditioner, and in particular, circulates a heat transfer medium without requiring a drive source such as a pump.
  • the present invention relates to a heat transfer device for performing heat transfer.
  • refrigerant circuit of an air conditioner there is known a refrigerant circuit provided with two systems of refrigerant circuits as disclosed in, for example, Japanese Patent Application Laid-Open No. 62-38951.
  • This type of refrigerant circuit includes a primary refrigerant circuit in which a compressor, a first heat source side heat exchanger, a pressure reducing mechanism, and a first use side heat exchanger are sequentially connected by refrigerant piping, a pump, and a second heat source side.
  • a secondary-side refrigerant circuit in which the heat exchanger and the second usage-side heat exchanger are sequentially connected by a refrigerant pipe.
  • the refrigerant evaporates in the first use side heat exchanger and condenses in the second heat source side heat exchanger.
  • the condensed refrigerant exchanges heat with room air in the second use-side heat exchanger and evaporates. This cools the room.
  • the refrigerant condenses in the first use side heat exchanger, and the refrigerant evaporates in the second heat source side heat exchanger.
  • the evaporated refrigerant exchanges heat with room air in the second use side heat exchanger and condenses. This heats the room.
  • the secondary-side refrigerant circuit in this heat transfer device is configured such that a heater, a condenser, and a closed vessel are connected in order by a refrigerant pipe, and the closed vessel is arranged at a position higher than the heater. Furthermore, the heater and the closed vessel are connected by a pressure equalizing pipe equipped with an on-off valve.
  • the on-off valve is closed, and the gas refrigerant heated by the heater is condensed by the condenser to liquefy, and then the liquid refrigerant is collected in the closed container. .
  • the on-off valve is opened and the heater and the sealed container are equilibrated by the equalizing pipe, and the liquid refrigerant is returned to the heater from the sealed container located at a higher position than the heater.
  • the heat transfer device described above suppresses a rise in pressure inside the closed vessel by improving the structure inside the closed vessel, but it cannot be said that sufficient reliability has been obtained.
  • the condenser in order to reliably introduce the liquid refrigerant into the closed container, the condenser must be placed at a higher position than the closed container, and there are many restrictions on the arrangement position of each device, and large scale It was difficult to apply it to a simple system or a long piping system.
  • the present invention has been made in view of this point, and has no need for a driving source.
  • An object of the present invention is to reduce restrictions on the arrangement position of devices and to obtain high reliability and versatility in the heat transfer system of the heat transfer system.
  • the present invention applies pressure to the refrigerant in the use-side refrigerant circuit, and circulates the refrigerant in the use-side refrigerant circuit using this pressure. Also, the refrigerant circulation direction is regulated so that the predetermined operation of the use side heat exchange means is performed.
  • the first solution taken by the present invention first comprises a heat source side heat exchange means (1) and a use side heat exchange means (3).
  • a heating operation for increasing the internal pressure of the heat source side heat exchange means (1) by applying heat to the refrigerant of the heat source side heat exchange means (1), and removing heat from the refrigerant of the heat source side heat exchange means (1).
  • one of the gas pipes (6) and the liquid pipe (7) is allowed to flow through the refrigerant and the other is prevented from flowing through the refrigerant.
  • the refrigerant is supplied from the heat source side heat exchange means (1) to the use side heat exchange means (3), and during the heat absorption operation, the use side heat exchange means (3) is supplied with the heat source side heat exchange.
  • Means (1) is provided with a refrigerant control means (G) for recovering the refrigerant and performing a heat absorbing operation or a heat radiating operation of the use side heat exchange means (3).
  • the refrigerant control means (G) allows one of the gas pipes (6) and the liquid pipe (7) to flow through the refrigerant and blocks the other refrigerant flow.
  • This allows the heat source side heat exchanger Refrigerant circulation in a predetermined direction is performed between the stage (1) and the use side heat exchange means (3), and the heat absorption operation or the heat radiation operation of the use side heat exchange means (3) is performed.
  • the refrigerant is circulated by the heat exchange performed in the heat source side heat exchange means (1).
  • the refrigerant of the heat source side heat exchanger means (1) is made to repeatedly perform ripening and heat radiation, and utilizing the pressure change of the refrigerant generated thereby, the heat source is used. Since the refrigerant is circulated between the side heat exchanger means (1) and the use side heat exchange means (3), no special transport means such as a refrigerant circulation pump for circulating the refrigerant is required. . As a result, it is possible to reduce the power consumption, reduce the number of locations where a failure occurs, and ensure the reliability of the entire device.
  • a second solution taken by the present invention is the first solution, wherein the refrigerant control means (G) heats the heat source means (A) when performing the heat absorbing operation of the use side heat exchange means (3).
  • the supply of liquid refrigerant from the heat source side heat exchange means (1) to the use side heat exchange means (3) through the liquid pipe (7) is allowed, and the heat source side heat exchange from the use side heat exchange means (3).
  • the heat-exchange means (3) moves from the use-side heat exchange means (3) to the heat-source heat exchange means (1).
  • the liquid refrigerant is supplied from the heat source side heat exchange means (1) to the use side heat exchange means (3), and the use side heat exchange means In the means (3), the liquid refrigerant evaporates.
  • This gas refrigerant is recovered from the use side heat exchange means (3) to the heat source side heat exchange means (1). Therefore, an endothermic operation can be obtained by the refrigerant evaporating in the use-side heat exchange means (3).
  • the heat source means (A) when the heat source means (A) performs the heating operation, Only the supply of liquid refrigerant from the source-side heat exchange means (1) to the use-side heat exchange means (3) is allowed, and the heat-source side heat exchange means (3) receives heat from the use-side heat exchange means (3) when the heat source means (A) absorbs heat.
  • the ripening operation of the use-side heat exchange means (3) is performed, so that the heat absorption operation can be performed reliably. Can be improved.
  • a gas refrigerant is supplied from the heat source side heat exchange means (1) to the use side heat exchange means (3).
  • this gas refrigerant condenses.
  • the liquid refrigerant is recovered by the heat exchange means (3) on the use side and the heat exchange means (1) on the heat source side. For this reason, a heat radiation operation is obtained by the refrigerant condensed in the use side heat exchange means (3).
  • a fourth solution taken by the present invention is the above-mentioned first solution, wherein the heat source side heat exchange means (1) comprises one or more first heat exchangers (la) and one or more second heat exchangers.
  • the internal pressure of the heated first heat exchanger (la) increases and this pressure acts on the second heat exchanger (lb).
  • the liquid refrigerant is supplied from the second heat exchanger (lb) to the use-side heat exchange means (3). That is, the first heat exchanger (la) generates a driving pressure for supplying the liquid refrigerant to the use-side heat exchange means (3).
  • the fourth solution only the first heat exchanger (la) is heated to increase the internal pressure of the first heat exchanger (la), and this pressure is changed to the second heat exchange (la).
  • the second heat exchanger (lb) to supply the liquid refrigerant from the second heat exchanger (lb) to the use-side heat exchange means (3), so that the first heat exchanger (la) Driving pressure for supplying the liquid refrigerant can be generated.
  • a reliable refrigerant supply operation can be performed while reducing the amount of heat given to the heat exchanger (la).
  • the fifth solution taken by the present invention is the above-mentioned first solution, wherein the heat source side heat exchange means (1) comprises one or more first heat exchangers (la) and one or more second heat exchangers. Exchangers (lb) are connected in parallel with each other.
  • the internal pressure of the first heat exchanger (la) that has absorbed heat decreases, and this pressure acts on the second heat exchanger (lb). Therefore, the liquid refrigerant is recovered from the use side heat exchange means (3) to the second heat exchanger (lb). That is, the first heat exchanger (la) generates a driving pressure for recovering the liquid refrigerant from the use-side heat exchange means (3).
  • heat is absorbed only from the first heat exchanger (la) to lower the internal pressure of the first heat exchanger (la), and the pressure is reduced to the second heat exchange (la).
  • the refrigerant control means (G) is provided in the gas pipe (6), and is opened when the heat source means (A) absorbs heat.
  • a first solenoid valve (SV1) that closes during the heating operation
  • a second solenoid valve (SV2) that is provided in the liquid pipe (7) and that opens during the heating operation of the heat source means (A) and closes during the heat absorbing operation. ).
  • a seventh solution taken by the present invention is the above-mentioned third or fifth solution, wherein the refrigerant control means (G) is provided in the gas pipe (6), and the heating operation of the heat source means (A) is performed.
  • a first solenoid valve (SV1) which is opened at the time of heat absorption and closed at the time of heat absorption operation, and a second solenoid valve provided at the liquid pipe (7) and opened at the time of heat absorption operation of the heat source means (A) and closed at the time of heating operation. (SV2).
  • the eighth solution taken by the present invention is the above-mentioned second or fourth solution, wherein the refrigerant control means (G) is provided in the gas pipe (6), and the use-side heat exchange means (3)
  • the first non-return valve (CV1) which allows only the flow of gas refrigerant to the heat source side heat exchange means (1), and the liquid pipe (7), and the heat source side heat exchange means (1)
  • a second check valve (CV2) that allows only the flow of the liquid refrigerant from the heat exchanger to the use-side heat exchange means (3).
  • a ninth solution of the present invention is as described in the third or fifth solution, wherein the refrigerant control means (G) is provided in the gas pipe (6), and the heat source side heat exchange means (1)
  • a first check valve (CV3) that allows only gas refrigerant to flow from the heat exchanger to the user-side heat exchange means (3) and a liquid pipe (7)
  • the second iiih valve (CV4) allows only the flow of the liquid refrigerant to the side heat exchange means (1).
  • the sixth to ninth solutions it is possible to specifically obtain the configuration of the refrigerant control means (G), and to perform the heat absorption operation or the heat radiation operation of the use side heat exchange means (3).
  • the setting of the refrigerant circulation direction can be performed accurately, and the reliability of the operation and the practicality can be improved.
  • the heat source side heat exchange means is connected in parallel to the heat source side heat exchange means.
  • the storage means (20) for recovering the liquid refrigerant of (1) is provided.
  • the liquid refrigerant of the heat source side heat exchange means (1) can be stored in the storage means (20), so that the heat source side heat exchange means (1)
  • the heat exchange efficiency can be set high, and the performance of the entire device can be improved.
  • the eleventh solution means adopted by the present invention is that the heat source side heat exchange means is constituted by a plurality of heat exchangers so that the heat radiation operation or the heat absorption operation of the use side heat exchange means can be continuously performed.
  • first heat source side heat exchange units (1A), one or more second heat source side heat exchange units (IB), and utilization side heat exchange means (3) included in one or more first heat source side heat exchange units (1A), one or more second heat source side heat exchange units (IB), and utilization side heat exchange means (3).
  • heat is given to the refrigerant in the first heat source side heat exchange section (U) to increase the internal pressure, and heat is taken from the refrigerant in the second heat source side heat exchange section (1B) to reduce the internal pressure.
  • Lowering the first heat exchange operation removing heat from the refrigerant in the first heat source side heat exchange section (1A) and lowering its internal pressure, and reducing the internal pressure of the refrigerant in the second heat source side heat exchange section (IB).
  • Heat source means (A) for alternately performing a second heat exchange operation of applying heat to increase the internal pressure is provided.
  • the first heat exchange of the heat source means (A) is performed.
  • the refrigerant is supplied from the first heat source side heat exchange section (1A) to the use side heat exchange means (3), and the second heat source side heat exchange section (IB) is supplied from the use side heat exchange means (3).
  • the refrigerant is supplied from the second heat source side heat exchange section (IB) to the use side heat exchange means (3), and the refrigerant is recovered from the use side heat exchange means (3).
  • the heat source side heat exchange section 1) is provided with a refrigerant control means (G) for recovering the refrigerant and performing a heat absorption operation or a heat radiation operation of the use side heat exchange means (3).
  • the refrigerant control unit (G) Plih distributes the refrigerant while alternately performing the first heat exchange operation and the second heat exchange operation of the heat source unit (A).
  • the heat source side heat exchange section that supplies the refrigerant to the use side heat exchange means (3) and the heat source side heat exchange section that collects the refrigerant from the use side heat exchange means (3) are alternately switched.
  • the heat absorption operation or the heat radiation operation of the use side heat exchange means (3) is performed continuously.
  • the heat source-side heat exchange section that supplies the refrigerant to the use-side heat exchange means (3), and the heat source-side heat that recovers the refrigerant from the use-side heat exchange means (3) Since the heat exchange section and the heat exchange section are alternately operated, the heat absorption operation or heat release operation of the user-side heat exchange means (3) can be continuously performed, so that the performance and practicality of the entire apparatus are improved. Can be.
  • the refrigerant control means (G) includes a heat source means (A) for performing the heat absorbing operation of the ripening side ripening means (3).
  • the liquid refrigerant is transferred from the first heat source side heat exchange section (1A) heated by the heat source means (A) to the use side heat exchange means (3) via the liquid pipe (7a).
  • the gas is supplied to the second heat source side heat exchange section (IB), which absorbs heat by the heat source means (A), so that the gas refrigerant is recovered from the use side heat exchange means (3) via the gas pipe (6b).
  • the second heat source side heated by the heat source means (A) during the second heat exchange operation of the heat source means (A)
  • a liquid refrigerant is supplied from the heat exchange section (IB) to the use side heat exchange means (3) via the liquid pipe (7b), while the first heat source absorbed by the heat source means (A) Refrigerant flows through the gas pipes (6a, 6b) and the liquid pipes (7a, 7b) so that the gas refrigerant is recovered from the use side heat exchange means (3) to the heat exchange section (U) via the gas pipe (6a).
  • the state is switched.
  • the first heat source side heat exchange section (1A) is connected to the use side heat exchange section.
  • the endothermic operation of the user-side heat exchange means (3) is performed continuously.
  • the use side heat exchange means (3) while supplying the liquid refrigerant from one heat source side heat exchange section (1A, IB) to the use side heat exchange means (3), the use side heat exchange means (3) Since the operation of recovering the gas refrigerant from the other heat source side heat exchange units (1A, 1B) is performed alternately, the heat absorption operation of the use side heat exchange means (3) can be performed continuously. Therefore, it is possible to improve the performance and practicality of the device itself.
  • the refrigerant control means (G) includes: When performing the heat dissipation operation of the means (3), during the first heat exchange operation of the heat source means (A), from the first heat source side heat exchange section (1A) heated by the heat source means (A), to the use side heat exchange.
  • the gas refrigerant is supplied to the means (3) via the gas pipe (6a), while the second heat source absorbed by the heat source means (A)
  • the refrigerant in the gas pipes (6a, 6b) and the liquid pipes (7a, 7b) is collected in the side heat exchange section (1B) so that the liquid refrigerant is recovered from the use side heat exchange means (3) through the liquid pipe (7b).
  • the second heat exchange unit (1B) is heated by the heat source means (A) during the second heat exchange operation of the heat source means (A).
  • the gas refrigerant is supplied through the gas pipe (6b) to the first heat source side heat exchange section (1A), where heat is absorbed by the heat source means (A).
  • the refrigerant flow state of the gas pipes (6a, 6b) and the liquid pipes (7a, 7b) is switched so that the liquid refrigerant is recovered via (7a).
  • the second heat source side while supplying gas refrigerant from the first heat source side heat exchange section (1A) to the use side heat exchange means (3), the second heat source side The operation of recovering the liquid refrigerant to the heat exchange section (1B) and the operation of the use side heat exchange section (3) while supplying the gas refrigerant from the second heat source side heat exchange section (1B) to the use side heat exchange section (3).
  • To the first heat source side heat exchange section (1A) and the operation of recovering the liquid refrigerant is performed alternately, and the heat radiation operation of the use side heat exchange means (3) is performed continuously.
  • each heat source side heat exchange section (U, 1B) is provided with one or more first heat exchangers (la). ) And one or more second heat exchangers (lb) configured in parallel with each other.
  • the internal pressure of the first heat exchanger (la) of the heat source side heat exchange section (1A, 1B) receiving heat from the heat source means (A) increases, and this pressure is increased by the second pressure.
  • the liquid refrigerant is supplied from the second heat exchanger (lb) to the use-side heat exchange means (3). That is, the first heat exchanger (la) generates a driving pressure for supplying the liquid refrigerant to the use-side heat exchange means (3).
  • the fourteenth solution only the first heat exchanger (la) is heated to increase the internal pressure of the first heat exchanger (la), and this pressure is changed to the second heat exchanger (la).
  • the second heat exchanger (lb) acts on the heat exchanger (lb) to supply the liquid refrigerant to the use-side heat exchange means (3), so that the first heat exchanger (la).
  • a driving pressure for supplying the liquid refrigerant can be generated.
  • each heat source side heat exchange section (1A, 1B) includes one or more first heat exchangers (la ) And one or more second heat exchangers aw are connected in parallel with each other.
  • the heat-source-side heat exchange section (1A, IB) from which heat is removed by the heat source means (A) during the heat-dissipating operation of the use-side heat exchange means (3), only the first heat exchanger (la) is used. Is cooled, the internal pressure of the heat exchanger (la) decreases, and this pressure is applied to the second heat exchanger (lb), and the use side heat exchange means (3) is applied to the heat exchanger (lb).
  • the liquid refrigerant is recovered from the tank via the liquid pipe (7).
  • the internal pressure of the first heat exchanger (la) of the heat source side heat exchange section (1A, IB) from which heat is taken off by the heat source means (A) decreases, and this pressure is reduced to the second pressure. Acts on the heat exchanger (lb). Therefore, the liquid refrigerant is recovered from the use-side heat exchange means (3) to the second heat exchanger (lb). That is, the first heat exchanger (la) generates a driving pressure for recovering the liquid refrigerant from the use-side heat exchange means (3).
  • heat is absorbed only from the first heat exchanger (la) to lower the internal pressure of the first heat exchanger (la), and the pressure is reduced to the second heat exchanger (la).
  • the liquid refrigerant is recovered from the use-side heat exchange means (3) to the second heat exchanger (lb) by acting on the heat exchanger (lb). Further, a driving pressure for recovering the liquid refrigerant can be generated. As a result, a reliable refrigerant recovery operation can be performed while reducing the heat exchanger (la) power and deprivation.
  • FIG. 1 is a diagram illustrating an overall configuration of a refrigerant circuit according to the first and second embodiments.
  • FIG. 2 is a diagram illustrating a secondary-side refrigerant circuit according to the third embodiment.
  • FIG. 3 is a diagram corresponding to FIG. 2 in the fourth embodiment.
  • FIG. 4 is a diagram corresponding to FIG. 2 in the fifth embodiment.
  • FIG. 5 is a diagram corresponding to FIG. 2 in the sixth embodiment.
  • FIG. 6 is a diagram illustrating a part of the secondary-side refrigerant circuit according to the seventh embodiment.
  • FIG. 7 is a diagram illustrating an entire secondary-side refrigerant circuit according to the seventh embodiment.
  • FIG. 8 is a diagram corresponding to FIG. 6 in the eighth embodiment.
  • FIG. 9 is a diagram corresponding to FIG. 7 in the eighth embodiment.
  • FIG. 10 is a diagram corresponding to FIG. 6 in the ninth embodiment.
  • FIG. 11 is a diagram corresponding to FIG. 6 in a modification of the ninth embodiment.
  • FIG. 12 is a diagram corresponding to FIG. 7 in the tenth embodiment.
  • FIG. 13 is a diagram corresponding to FIG. 1 in the eleventh embodiment.
  • FIG. 14 is a diagram illustrating a first cooling operation state in the eleventh embodiment.
  • FIG. 15 is a diagram showing a second cooling operation state in the first embodiment.
  • FIG. 16 is a diagram showing a first heating operation state in the eleventh embodiment.
  • FIG. 17 is a diagram showing a second heating operation state in the first embodiment.
  • FIG. 18 is a diagram corresponding to FIG. 7 in the 12th embodiment.
  • FIG. 19 is a diagram corresponding to FIG. 1 showing a cooling operation state in the thirteenth embodiment.
  • FIG. 20 is a diagram corresponding to FIG. 1 showing a heating operation state in the thirteenth embodiment.
  • FIG. 21 is a diagram showing a cooling operation state in the fourteenth embodiment.
  • FIG. 22 is a diagram showing a heating operation state in the fourteenth embodiment.
  • Each of the embodiments includes two refrigerant circuits, a primary refrigerant circuit and a secondary refrigerant circuit, and uses the amount of heat given from the primary refrigerant circuit to the secondary refrigerant circuit to perform the secondary refrigerant circuit.
  • the refrigerant is circulated in the side refrigerant circuit.
  • the present invention is applied to a refrigerant circuit of an air conditioner that circulates the refrigerant to perform indoor air conditioning.
  • FIG. 1 shows a refrigerant circuit of the entire heat transfer device of the present embodiment.
  • the present refrigerant circuit has a configuration in which the refrigerant in the primary-side refrigerant circuit (A) as a heat source means and the refrigerant in the two-sided refrigerant circuit (B) exchange heat and heat.
  • the secondary-side refrigerant circuit (B) for cooling the room by exchanging heat with the room air will be described.
  • the secondary-side refrigerant circuit (B) transfers heat between the indoor-side heat exchanger (3) as a use-side heat exchange means disposed in the air conditioning room and the primary-side refrigerant circuit (A).
  • Heat source side heat exchange The secondary heat source heat exchanger (1) as the exchange means is connected by a gas pipe (6) and a liquid pipe (7), and is configured as a closed circuit in which the refrigerant circulates.
  • the gas pipe (6) is above the indoor heat exchanger (3) and the secondary heat source heat exchanger (1), and the liquid pipe (7) is the indoor heat exchanger (3) and the secondary heat source heat exchanger. Each is connected to the lower part of (1).
  • the above-mentioned gas pipe (6) has the power of the first solenoid valve (SV1) ⁇ and the liquid pipe (7) has the second solenoid valve (SV1).
  • SV2 are provided, and an indoor electric expansion valve (EV1) is provided between the indoor heat exchanger (3) and the second solenoid valve (SV2) in the liquid pipe (7).
  • EV1 indoor electric expansion valve
  • SV1, SV2 constitute the refrigerant control means (G).
  • the primary refrigerant circuit (A) as a heat source means for supplying heat to the secondary refrigerant circuit (B) will be described.
  • the primary refrigerant circuit (A) is connected to the compressor (11), the four-way switching valve (22), the outdoor heat exchanger (14), and the primary heat source heat exchanger L2) via the refrigerant pipe (16). It is composed.
  • the outdoor heat exchanger (14) is connected to the discharge side of the compressor (11) by the switching operation of the four-way switching valve (22).
  • the state in which the compressor (12) is connected to the suction side of the compressor (11), respectively the state shown by the solid line in FIG.
  • first and second outdoor electric expansion valves (EV2, EV3) are provided.
  • the solenoid valves (SV1, SV2), electric expansion valves (EV1, EV2, EV3) and four-way selector valve (22) are controlled to open and close by a controller (C).
  • C controller
  • the four-way switching valve (22) is switched to the solid line side, the first outdoor electric expansion valve (EV2) is fully opened, and the second Adjust the opening of the outdoor electric expansion valve (EV3) to the specified opening.
  • the first solenoid valve (SV1) is opened and the second solenoid valve (SV2) is closed.
  • the compressor (11) is driven, and in the primary-side refrigerant circuit (A), the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is discharged as shown by the solid line arrow in FIG.
  • the refrigerant in the secondary-side heat source heat exchanger (1) which has lost heat by exchanging heat with the primary-side heat source heat exchanger (12) Is condensed, and the internal pressure of the secondary heat source heat exchanger (1) decreases. Due to the pressure difference between the secondary side heat source heat exchanger (1) and the indoor heat exchanger (3), the gas refrigerant in the indoor side heat exchanger (3) is passed through the gas pipe (6) to the secondary side heat source heat exchanger. Collected in exchanger (1).
  • the gas refrigerant recovered in the secondary-side heat source heat exchanger (1) is cooled by the refrigerant flowing through the primary-side heat source heat exchanger (12) to become a liquid refrigerant, and this secondary-side heat source heat exchanger ( Store in 1).
  • a switching operation is performed in each of the refrigerant circuits (A, B), the four-way switching valve (22) is switched to the broken line side, the second outdoor electric expansion valve (EV3) is fully opened, and the first outdoor is operated. While opening the electric expansion valve (EV2) to a predetermined opening, the first solenoid valve (SV1) is closed and the second solenoid valve (SV2) is opened.
  • the primary refrigerant circuit (A) the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is converted into the primary heat source heat exchanger (12) as shown by the broken arrow in FIG.
  • heat is exchanged between the secondary heat source heat exchanger (1) and the refrigerant in the secondary heat source heat exchanger (1) is condensed by applying heat, and then the first outdoor electric expansion valve (BV2 ), The heat is exchanged with the outside air in the outdoor heat exchanger (14) to evaporate, and then returns to the compressor (11). This cycle is repeated.
  • the secondary-side refrigerant circuit (B) heat is exchanged with the primary-side heat source heat exchanger CL2) and heat is given to the refrigerant in the secondary-side heat source heat exchanger (1). Partially evaporates, and the internal pressure of the secondary heat source heat exchanger (1) rises at. Due to the pressure difference between the secondary heat source heat exchanger (1) and the indoor heat exchanger (3), the liquid refrigerant in the secondary heat source heat exchanger (1) is converted into the secondary heat source heat exchanger ( It is pushed out from the lower part of 1) to the indoor heat exchanger (3) via the liquid pipe (7). The liquid refrigerant extruded into the indoor heat exchanger (3) is decompressed by the indoor electric expansion (EV1), exchanges heat with the indoor air in the indoor heat exchanger (3), evaporates, and cools the indoor air. I do.
  • EV1 indoor electric expansion
  • each refrigerant circuit (A, B) is performed alternately, and the refrigerant circulates in the secondary refrigerant circuit (B) to cool the room. Therefore, in the present embodiment, heat transfer can be performed in the secondary-side refrigerant circuit (B) without providing a drive source such as a pump in the secondary-side refrigerant circuit (B). For this reason, it is possible to reduce power consumption, reduce the number of locations where a failure occurs, and ensure the reliability of the entire device.
  • the operation of absorbing and dissipating heat in the secondary-side refrigerant circuit (B) is performed stably, even if the size of the secondary-side refrigerant circuit (B) is large, the refrigerant circulation can be performed well, and the Enlargement can be achieved.
  • the circuit of this embodiment has the same circuit configuration as that of the above-described first embodiment, and constitutes an air conditioner dedicated to heating.
  • the four-way switching valve (22) is switched to the solid line side, the first outdoor electric expansion valve (EV2) is fully opened, and the second Adjust the opening of the outdoor electric expansion valve (EV3) to the specified opening.
  • the first solenoid valve (SV1) is closed and the second solenoid valve (SV2) is opened.
  • the primary refrigerant circuit (A) As a result, in the primary refrigerant circuit (A), as indicated by the solid arrow, the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is condensed in the outdoor heat exchanger (14), (2) The pressure is reduced at the electric expansion valve (EV3), heat exchanges with the secondary heat source heat exchanger (1) at the primary heat source heat exchanger (12), evaporates, and returns to the compressor (11). .
  • This circulation Repeat the ring operation.
  • the secondary-side heat is removed from the primary-side heat source heat exchanger (12) and heat is taken away.
  • the refrigerant in the heat source heat exchanger (1) condenses, and the internal pressure of the secondary heat source heat exchanger (1) decreases. Due to the pressure difference between the secondary heat source heat exchanger (1) and the indoor heat exchanger (3), the liquid refrigerant of the indoor heat exchanger (3) is heated via the liquid pipe (7). Collected in exchanger (1).
  • the primary-side refrigerant circuit (A) the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is condensed in the primary-side heat source heat exchanger (12), as indicated by the dashed arrow. Then, the pressure is reduced in the first electric expansion valve (EV2), evaporated in the outdoor heat exchanger (14), and returned to the compressor (11). This circulation operation is repeated.
  • EV2 first electric expansion valve
  • the secondary side refrigerant circuit (B) As shown by the two-dot chain line arrow, heat was given through a mature exchange with the 1-side heat source heat exchanger (12).
  • the refrigerant in the secondary heat source heat exchanger (1) evaporates, and the internal pressure of the secondary heat source heat exchanger (1) rises. Due to the pressure difference between the secondary side heat source heat exchanger (1) and the indoor heat exchanger (3), the gas refrigerant in the secondary side heat source heat exchanger (1) is changed to the secondary side heat source heat exchanger (1).
  • the gas refrigerant supplied to the indoor heat exchanger (3) exchanges heat with the indoor air in the indoor heat exchanger (3), condenses, and heats the indoor air.
  • the secondary-side refrigerant circuit (B) of the present embodiment is provided with a check valve (CV1, CV2) instead of the solenoid valve (SV1, SV2) of the first embodiment described above. It constitutes the secondary refrigerant circuit (B) of the air conditioner.
  • the gas pipe (6) is connected to the indoor heat exchanger (3) to transfer the gas refrigerant from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1).
  • a non-return valve (CV1) which allows only circulation, is used to supply only the liquid refrigerant to the secondary heat source heat exchanger (1) and the inside heat exchanger (3) to the liquid pipe (7).
  • a permissible check valve (CV2) is provided for each.
  • the primary refrigerant circuit At the time of the cooling operation of the present embodiment, the primary refrigerant circuit
  • the solenoid valve is not provided in the secondary refrigerant circuit (B), that is, the four-way switching valve (22) and the electric expansion valves (EV2, EV3) of the primary refrigerant circuit (A) are not provided. ), The refrigerant in the secondary refrigerant circuit (B) is circulated.
  • the secondary-side refrigerant circuit (B) of this embodiment is provided with a check valve in place of the solenoid valves (SV1, SV2) of the second embodiment described above.
  • the gas pipe (6) is connected to the gas refrigerant (2) from the secondary heat source heat exchanger (1) to the indoor heat exchanger (3).
  • a check valve (CV3) that allows only circulation allows only liquid refrigerant to flow from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1) in the liquid pipe (7).
  • a check valve (CV4) is provided for each.
  • the refrigerant circulates in the secondary refrigerant circuit (B) (the chain line in Fig. 2). And the arrow indicated by the two-dot chain line).
  • the solenoid valve is not provided in the secondary refrigerant circuit (B), that is, the four-way switching valve (22) and the electric expansion valve (EV2.EV3) of the primary refrigerant circuit (A) are not provided.
  • the refrigerant in the secondary refrigerant circuit (B) is circulated only by performing the switching operation.
  • the secondary-side refrigerant circuit (B) of the present embodiment is provided with a check valve in each pipe (6, 7) and a secondary-side heat source heat exchanger (1) connected to a pair of heat exchangers (la, lb). It consists of. And, in the present embodiment, the secondary-side refrigerant circuit (B) of the air conditioner dedicated for cooling is configured.
  • the gas pipe (6) is connected to the indoor heat exchanger (3) by the secondary heat source.
  • a check valve (CV1) that allows only gas refrigerant to flow to the heat exchanger (1) has a liquid pipe (7) connected from the secondary heat source heat exchanger (1) to the indoor heat exchanger (3).
  • Check valves (CV2) that allow only the flow of liquid refrigerant to) are provided.
  • the above-mentioned secondary heat source heat exchanger (1) is configured by connecting the first and second secondary heat exchangers (la, lb) in parallel, and each heat exchanger (la, lb) is Exchanges heat with the primary heat source heat exchanger (12).
  • the primary heat source heat exchanger (12) is composed of a pair of heat exchangers (12a, 12b) corresponding to each secondary heat source heat exchanger (la, lb). (12a, 12b) individually exchange heat with the secondary heat source heat exchanger (la, lb).
  • the first secondary heat source heat exchanger (la) is formed smaller than the second secondary heat source heat exchanger (lb).
  • the refrigerant circulation operation of the secondary refrigerant circuit (B) during the cooling operation is as follows.
  • each secondary heat source heat exchanger (la, lb), which has lost heat by exchanging heat with the refrigerant evaporating in each primary heat source heat exchanger (12a, 12b), condenses, and Within heat exchanger (la, lb)
  • the pressure drops.
  • the gas refrigerant in the indoor heat exchanger (3) is recovered to each secondary-side heat source heat exchanger (la, lb) via the gas pipe (6) as indicated by the solid line arrow in Fig. 4. It is cooled and stored as liquid refrigerant.
  • the secondary heat source heat exchanger (1) is composed of a pair of heat exchangers (la, lb), and one of them stores the liquid refrigerant to be supplied to the indoor heat exchanger (3).
  • the other is for generating pressure as a driving force for supplying the liquid refrigerant.
  • the secondary-side refrigerant circuit (B) of the present embodiment is provided with a check valve in each pipe (6, 7) and a secondary-side heat source heat exchanger (1) connected to a pair of heat exchangers (la, lb). It consists of.
  • the secondary refrigerant circuit (B) of the air conditioner dedicated to cooling is configured.
  • the gas pipe (6) is connected from the secondary heat source heat exchanger (1) to the indoor
  • a non-return valve (CV3) that allows only gas refrigerant to flow to the heat exchanger (3) is installed in the liquid pipe (7) from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1).
  • Check valves (CV4) that allow only the flow of liquid refrigerant to) are provided.
  • the secondary heat source heat exchanger (1) is the same as that of the above-mentioned cooling only unit.
  • the refrigerant circulation operation of the secondary refrigerant circuit (B) during the heating operation is as follows.
  • the secondary-side refrigerant circuit (B) of the present embodiment is provided with a plurality of secondary-side heat source heat exchangers (1) including the pair of heat exchangers (la, lb) described in the above-described fifth embodiment ( In the present embodiment, two of them) constitute a secondary refrigerant circuit (B) of an air conditioner dedicated to cooling.
  • the secondary-side refrigerant circuit (B) will be described.
  • the gas pipe (6) and the liquid pipe (7) are branched into two branch pipes (6a, 6b, 7a, 7b), respectively, and each branch pipe (6a, 6b) of the gas pipe (6) is branched.
  • Each branch pipe (7a, 7b) of the liquid pipe (7) has a check valve that allows only the flow of liquid refrigerant from the secondary heat source heat exchanger (1A, IB) to the indoor heat exchanger (3).
  • CV2, CV2 Two branch pipe (6a, 6b) of the gas pipe (6)
  • Each secondary heat source heat exchanger (U, 1B) is composed of the first and second primary heat exchangers (la, lb) connected in parallel, and each heat exchanger (la, lb) Exchanges heat with the primary heat source heat exchanger (not shown) (see Fig. 4).
  • the refrigerant circulation operation of the secondary refrigerant circuit (B) during the cooling operation will be described.
  • the refrigerant is condensed (radiation operation) in one of the secondary heat source heat exchangers (U)
  • the refrigerant is evaporated (heat absorption operation) in the other secondary heat source heat exchanger (IB).
  • the primary-side refrigerant circuit (A) is switched so that the operation is performed.
  • a continuous refrigerant circulation operation is performed.
  • the secondary-side mature-source heat exchanger (1A) located on the left side in Fig. 6 is in a heat radiation state and the gas refrigerant is recovered from the indoor heat exchanger (3) (Fig. (See the arrow shown by the solid line.)
  • the first secondary heat source heat exchanger (la) of the secondary heat source heat exchanger (1B) located on the right side is in an endothermic state.
  • the internal pressure acts on the second secondary heat source heat exchanger (lb) as the internal pressure increases due to the evaporation of the refrigerant, and the second secondary heat source heat exchanger (lb) is The liquid refrigerant is supplied to the heat exchanger (3) (see the arrow indicated by the broken line in FIG. 6).
  • FIG. 7 shows a circuit in which such a secondary refrigerant circuit (B) is applied to a so-called indoor multi-unit in which a plurality of indoor heat exchangers (3) are arranged.
  • (F ') in Fig. 7 is an indoor fan.
  • each secondary-side heat source heat exchanger (1A, 1B) is constituted by first and second two primary-side heat exchangers (la, lb). It may be constituted by a heat exchanger.
  • the secondary-side refrigerant circuit (B) of this embodiment is provided with a plurality of secondary-side heat source heat exchangers (1) each including a pair of heat exchangers (la, lb), as in the seventh embodiment. (Two in this embodiment) constitute a secondary refrigerant circuit (B) of an air conditioner dedicated to heating.
  • each branch pipe (6a, 6b) of the gas pipe (6) has a gas refrigerant flowing from the secondary heat source heat exchanger (1A, 1B) to the indoor heat exchanger (3).
  • Non-return valves (CV3, CV3) are provided to allow only one.
  • Each branch pipe (7a, 7b) of the liquid pipe (7) has a check valve that allows only the flow of liquid refrigerant from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1A, 1B). (CV4, CV4) is provided.
  • CV4, CV4 is provided.
  • the refrigerant circulation operation of the secondary-side refrigerant circuit (B) during the heating operation will be described.
  • the heat dissipation operation is performed in one secondary-side heat source heat exchanger (1A)
  • the other secondary-side heat source heat exchanger (IB) is used.
  • Switch the primary refrigerant circuit (A) so that heat absorption operation is performed.
  • the heat radiating state and the heat absorbing state of the two secondary-side heat source heat exchangers (U, 1B) are alternately and alternately repeated, thereby performing a continuous refrigerant circulation operation.
  • the first secondary heat source heat exchanger (la) of the secondary heat source heat exchanger (U) located on the left side in Fig. 8 is in a heat radiation state, and this low pressure is applied to the second secondary heat exchanger (U). It acts on the heat source heat exchanger (lb) to recover the liquid refrigerant from the indoor heat exchanger (3) (see the dashed line arrow in Fig. 6).
  • the secondary heat source heat exchanger (1B) located on the right side absorbs heat and supplies gas refrigerant to the indoor heat exchanger (3) (see the arrow indicated by the two-dot chain line in FIG. 6).
  • FIG. 9 shows a circuit in which such a secondary refrigerant circuit (B) is applied to a so-called indoor multi-unit in which a plurality of indoor heat exchangers (3) are arranged.
  • each secondary-side heat source heat exchanger (1A, 1B) is constituted by first and second two primary-side heat exchangers (la, lb). It may be configured with a single heat exchanger.
  • the secondary-side refrigerant circuit (B) of the present embodiment is different from the secondary-side refrigerant circuit (B) dedicated to cooling shown in the fifth embodiment described above in that each secondary-side heat source heat Exchanger (la, lb) in parallel with a receiver (20).
  • each heat source side heat exchanger (la, lb) when each heat source side heat exchanger (la, lb) is in a heat radiation state and the indoor heat exchanger (3) recovers and condenses the gas refrigerant, the condensed liquid The refrigerant can be stored in the receiver (20).
  • the amount of liquid refrigerant stored in the secondary heat source heat exchanger (la, lb) can be reduced. Therefore, a large heat exchange area can be secured, the heat exchange efficiency can be improved, and the performance of the entire device can be improved.
  • the same liquid receiver (20) is provided in the secondary-side refrigerant circuit (B) dedicated to heating shown in the above-described sixth embodiment. Also in this configuration, when each heat source side heat exchanger (la, lb) becomes a heat absorbing state and recovers the liquid refrigerant from the indoor heat exchanger (3), the liquid refrigerant is retained in the receiver (20). be able to. With this, a large heat exchange area can be secured, and the performance of the entire apparatus can be improved. 1st 10th Embodiment 1
  • the secondary-side refrigerant circuit (B) including the plurality of secondary-side heat source heat exchangers (1A, 1B) shown in the seventh and eighth embodiments indoor cooling and heating are performed.
  • This is a so-called heat pump circuit that can be used.
  • only the differences from the refrigerant circuits shown in the seventh and eighth embodiments will be described.
  • the branch pipes (6a, 6b) of the gas pipe (6) are divided into cooling branch pipes (6a-C, 6b-C) and heating branch pipes (6a-W, 6b-W, respectively).
  • the cooling branch pipe (6a-C. 6b-C) has a check valve that allows only gas refrigerant to flow from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1A, IB).
  • CV 1 and a solenoid valve (SVC-1) that opens during cooling operation and closes during heating operation.
  • the heating branch pipes (6a-W, 6b-O) have a non-return that allows only gas refrigerant to flow from the secondary heat source heat exchangers (1A, 1B) to the indoor heat exchanger (3).
  • the branch pipes (7a, 7b) of the liquid pipe (7) are branched into cooling branch pipes (7a-C, 7b-C) and heating branch pipes (7a-W, 7b-W), respectively.
  • the heating branch pipe (7a-W, 7b-W) has a reverse flow that allows only the flow of liquid refrigerant from the indoor heat exchanger (3) to the secondary heat source heat exchanger (1A, 1B).
  • a stop valve (CV 3) and a solenoid valve (SVW-2) that opens during heating operation and closes during cooling operation are provided.
  • the condition of 1 is that the solenoid valve (SVC-1) connected to the secondary heat source heat exchanger (IB) located on the right side and the solenoid valve (SVC-1) connected to the secondary heat source heat exchanger (1A) located on the left side SVC-2) is opened and other solenoid valves are closed.
  • the solenoid valve (SVC-2) connected to the secondary heat source heat exchanger (IB) located on the right and the solenoid valve (SVC-2) connected to the secondary heat source heat exchanger (1A) located on the left SVC-1) is opened and other solenoid valves are closed.
  • the two states are alternately switched to perform the same refrigerant circulation operation as in the above-described seventh embodiment, thereby cooling the room.
  • the state 1 during the indoor heating operation is as follows: the solenoid valve (SVW-1) connected to the secondary heat source heat exchanger (1B) located on the right side and the secondary heat source heat exchanger ( The solenoid valve (SVW-2) connected to 1A) is opened and the other solenoid valves are closed.
  • the solenoid valve (SVW- 2) that is located on the secondary heat source heat exchanger (IB) located on the right side and the solenoid valve (SVW- 2) that is located on the secondary heat source heat exchanger (1A) located on the left side 1) is open and other solenoid valves are closed.
  • the switching operation of the valve (SVC-l. SVC-2. SVW-1. It is possible to obtain a highly practical air conditioner that is set.
  • each secondary-side heat source heat exchanger aA, IB) is constituted by first and second two primary-side heat exchangers (la, lb). It may be composed of individual heat exchangers.
  • a primary refrigerant circuit As shown in FIG. 13, in the present embodiment, as a primary refrigerant circuit (A), an outdoor heat source in which a compressor (11), a four-way switching valve (22), and an outdoor fan (F) are arranged in close proximity. It has an exchanger (14), an outdoor electric expansion valve (EV), and a primary heat source heat exchanger (12A, 12B) composed of multiple heat exchangers.
  • a gas-side pipe (24) is connected to one end of the outdoor heat exchanger (14) on the gas side, and a liquid-side pipe (25) is connected to the other end of the outdoor heat exchanger (14).
  • the gas side pipe (24) is switched between the discharge side and the suction side of the compressor (11) by the four-way switching valve (22). That is, the gas side pipe (24) is connected to the discharge gas line (24a) connecting the discharge side of the compressor (11) and the four-way switching valve (22), and to the suction side of the compression mechanism (21).
  • the intake gas line (24b) connecting to the switching valve (22) is protected.
  • the intake gas line (24b) is provided with an accumulator (28).
  • the liquid side pipe (25) is provided with the above-mentioned outdoor electric expansion valve (EV), and one end is branched to the outdoor heat exchanger (14) and the other end is branched to each of the primary side heat source heat exchangers (12a to 12c). Connected to each other.
  • the liquid side pipe (25) includes a main liquid pipe (25A) and a branch liquid pipe (25a to 25c) branched from the main liquid pipe (25A). Each of the branch liquid pipes (25a to 25c) Are connected to each primary heat source heat exchanger (12a to 12c).
  • the primary refrigerant circuit (A) includes a discharge line (30) connecting the discharge side of the compressor (11) and each of the primary heat source heat exchangers (12a to 12c), A suction line (31) is provided for collecting gas refrigerant from the heat source heat exchangers (12a to 12c) on the suction side of the compressor (11).
  • the three heat exchangers (12a to 12c) on the left side in FIG. 13 correspond to the tenth embodiment (see FIG. 12) described above.
  • This is a first primary heat source heat exchanger (12A) that exchanges heat with the left secondary heat source heat exchanger (1A).
  • the three right heat exchangers (12a to 12c) are the second primary heat source side heat exchangers that exchange heat with the right secondary heat source heat exchanger (1B) in the tenth embodiment. (12B).
  • each primary heat source heat exchanger (12A, 12B) Since the configuration of each primary heat source heat exchanger (12A, 12B) is substantially the same, here, each piping (25a to 25c, 30, 31) to one secondary heat source heat exchanger (12A) is used. ) Will be described.
  • [ ⁇ , the first, second, and third heat exchangers (12a to 12c) are called in order from the one located on the right side.
  • the lower end of the first heat exchanger (12a) is connected to a first branch liquid pipe (25a) branched from the main liquid pipe (25A) and provided with a capillary tube (CP).
  • a first liquid pipe (25d) is connected between the capillary tube (CP) and the first heat exchanger (12a) in the first branch liquid pipe (25a).
  • the other end of the liquid pipe (25d) is connected to the main liquid pipe (25A), and the check valve (CV3) allows only the flow of liquid refrigerant flowing from the first heat exchanger (12a) to the main liquid pipe (25A).
  • the upper end of the first heat exchanger (12a) is connected to the discharge line (30) by the first gas pipe (30a) and to the suction line (31) by the second gas pipe (31a). I have.
  • Each of these gas pipes (30a, 31a) is provided with a solenoid valve (SV3, SV4).
  • the lower end of the second heat exchanger (12b) branches off from the main liquid pipe (25A) and only allows the flow of the liquid refrigerant flowing from the second heat exchanger (12b) to the main liquid pipe (25A). It is connected to the second branch fluid pipe (25b) with an allowed check valve (CV4).
  • the upper end of the second heat exchanger (12b) is connected to the discharge line (30) by a third gas pipe (30b).
  • the third gas pipe (30b) is provided with a solenoid valve (SV5).
  • the third heat exchanger (12c) has a lower end that branches off from the main liquid pipe (25A) and only allows the flow of the liquid refrigerant flowing from the main liquid pipe (25A) to the third heat exchanger (12c). It is connected to the third branch liquid pipe (25c) equipped with an allowed check valve (CV5) and a capillary tube (CP). The upper end of the third heat exchanger (12c) is connected to the suction line (31) by a fourth gas pipe (31b). The fourth gas pipe (31b) is also provided with a solenoid valve (SV6).
  • SV6 solenoid valve
  • One end of a first connection pipe (32) is connected between the second heat exchanger (12b) and the check valve (CV4) in the second branch liquid pipe (25b), and the first connection pipe (32 The other end is connected between the third heat exchanger (12c) and the capillary tube (CP) in the third branch liquid pipe (25c).
  • One end of a second connection pipe (33) is connected between the second heat exchanger (12b) and the solenoid valve (SV5) in the third gas pipe (30b), and is connected to the second connection pipe (33). The other end is connected between the third heat exchanger (12c) and the solenoid valve (SV6) in the fourth gas pipe (31b).
  • the secondary refrigerant circuit (B) is the same as that described in the tenth embodiment.
  • the right small-sized first secondary-side heat source heat exchanger (la) force ⁇ adjacent to the first heat exchanger (12a).
  • the large heat exchanger (lb) on the left side consists of a pair of second and third secondary heat source heat exchangers (lb, lb ') connected in parallel to each other, and the second and third heat exchangers The heat exchanger is adjacent to the vessel (12b, 12c).
  • these heat exchangers (la, lb, lb ') are connected in parallel with each other, and the upper end is connected to the branch pipe (6a, 6b) of the gas pipe (6), and the lower end is connected to the liquid pipe (7). They are connected to branch pipes (7a, 7b), respectively.
  • the four-way switching valve (22) is switched to the solid line side in the primary refrigerant circuit (A) as the first cooling operation state, and the second primary heat source side heat exchange is performed.
  • This liquid refrigerant exchanges heat with each of the heat exchangers (la, lb, lb ') of the first secondary heat source side heat exchanger (1A), and the heat exchangers (la, lb, After removing heat from the lb ') refrigerant and evaporating, it returns to the compressor (11) through the suction line (31).
  • the other part of the refrigerant discharged from the compressor (11) is connected to the second primary side from the discharge line (30).
  • the heat flows into the first heat exchanger (12a) of the heat source heat exchanger (12B) and exchanges heat with the first heat exchanger (la) of the second secondary heat source side heat exchanger (IB).
  • the condensation (radiation operation) of the refrigerant is performed ⁇ the second secondary heat source
  • the refrigerant evaporates (heat-absorbs), so the first heat exchanger of the second secondary heat source heat exchanger (1B)
  • the internal pressure of (la) rises. This pressure acts on the second and third heat exchangers (lb, lb ') of the second secondary heat source heat exchanger (1B), and as shown by the dashed arrows in FIG. Is supplied from each of these heat exchangers (la.
  • the heat exchanger (la, lb) of the first secondary-side heat source heat exchanger (1A) passes through the branch pipe (6a) of the gas pipe (6). , lb ').
  • the gas refrigerant recovered in each of the heat exchangers (la, lb, lb ') flows between the heat exchangers (12a.12b, 12c) of the first primary heat source heat exchanger (12A). The heat is exchanged at the, and it is condensed and stored as liquid refrigerant.
  • each refrigerant circuit (A, B) a switching operation is performed in each refrigerant circuit (A, B), and a radiation and heat absorption operation in each secondary-side heat source heat exchanger (U, 1B) is performed. Replace it.
  • the refrigerant flowing from the second secondary heat source heat exchanger (1B) to the indoor heat exchanger (3) flows through the first secondary heat source heat exchanger QA.
  • the circulation operation of the refrigerant collected in ()) is performed.
  • the first gas pipe (30) in the first primary heat source side heat exchanger (12A) is set.
  • the solenoid valve (SVW-1) which is used for the secondary-side heat source heat exchanger (1A) located on the left side and the secondary-side heat source heat exchanger located on the right side Open the solenoid valve (SVW-2) that descends to (IB) and close other solenoid valves.
  • the refrigerant discharged from the compressor (11) is discharged into the discharge line (30) in the primary refrigerant circuit (A) as shown by a solid line arrow in FIG. From the first primary heat source side heat exchanger (12A) to the heat exchangers (12a to 12c) of the first secondary heat source side heat exchanger (1A). lb, lb ') and exchanges heat with the refrigerant in this heat exchanger (la, lb, lb') to condense.
  • the refrigerant of the first heat exchanger (la) is supplied to the first branch liquid pipe (25a) and the first liquid pipe (25d), and the refrigerant of the second and third heat exchangers (lb, lb ') is supplied to the first branch.
  • the liquid refrigerant flowing into the main liquid pipe (25A) flows into the first heat exchanger (12a) of the second primary heat source side heat exchanger (12B), and flows into the second secondary heat source side.
  • the second gas pipe (31a) and the suction port Return to the compressor (11) via the line (31).
  • the refrigerant is evaporated (heat-absorbing operation) in the first secondary-side heat source heat exchanger (1A), and the second secondary-side heat source heat is exchanged.
  • the first heat exchanger (la) of the heat exchanger (IB) refrigerant is condensed (radiation operation), so each heat exchanger (1A) of the first secondary heat source heat exchanger (1A) la. lb, lb ').
  • the gas refrigerant from each of the heat exchangers (la, lb, lb ') is supplied to the indoor heat exchanger (3) from the branch pipe (6a) of the gas pipe (6), and the indoor heat exchanger (3). After being condensed in 3), it is collected in each heat exchanger (la, lb, 1) of the second secondary heat source heat exchanger (1B) through the branch pipe (7b) of the liquid pipe (7).
  • each refrigerant circuit ( ⁇ , ⁇ ) a switching operation is performed in each refrigerant circuit ( ⁇ , ⁇ ), and a heat radiation and heat absorption operation in each secondary heat source heat exchanger (1A, IB) is performed. Is replaced.
  • the refrigerant introduced from the second secondary heat source heat exchanger (IB) into the indoor heat exchanger (3) is the first secondary heat source heat exchanger.
  • the refrigerant circulates in (1A).
  • the indoor cooling operation and the heating operation are arbitrarily set and the continuous operation is performed, so that a highly practical air conditioner can be obtained.
  • Twelfth embodiment one This embodiment is provided with a plurality of indoor heat exchangers (3, 3,%) Individually arranged in a plurality of rooms, each having a power ⁇ a so-called cooling / heating free-flow system capable of individually selecting a cooling operation and a heating operation. It constitutes the secondary refrigerant circuit (B) of the multi-type air conditioner.
  • B secondary refrigerant circuit
  • the secondary refrigerant circuit (B) includes first and second two gas pipes (6A, 6B), and a cooling gas branch in the first gas pipe (6A).
  • the pipes (6a-C, 6b-C) are connected to the second gas pipe (6B), and the branch pipes for heating (6a-W, 6b-W).
  • the gas side piping (3A) of each indoor heat exchanger (3, 3 .7) is branched into the first connecting pipe (3A-1) and the second connecting pipe (3A-2), and the first connecting pipe (3A-1) is connected to the first gas pipe (6A), and the second connection pipe (3A-2) is connected to the second gas pipe (6B).
  • Each connection pipe (3A-1, 3A-2) is provided with a solenoid valve (SV7, SV8).
  • SV7, SV8 solenoid valve
  • the condition of (1) is that the solenoid valve (SVC-1) connected to the secondary heat source heat exchanger (1A) located on the left side and the solenoid valve (SVC-1) connected to the secondary heat source heat exchanger (IB) located on the right side SVC-2) is open and other solenoid valves are closed.
  • the solenoid valve (SVC-2) leading to the secondary heat source heat exchanger (U) located on the left and the solenoid valve (B) leading to the secondary heat source heat exchanger (IB) located on the right SVC-1) is opened and other solenoid valves are closed.
  • the two states are alternately switched.
  • each indoor heat exchanger (3, 3, 7) is a heating requirement (for example, there are more indoor heat exchangers that perform heating operation than cooling-operated indoor heat exchangers) Is the case), is switched to two states.
  • the condition of (1) is that the solenoid valve (SVW-1) installed on the secondary-side heat source heat exchanger (1A) located on the left side and the solenoid valve (II) on the secondary-side heat source heat exchanger (IB) located on the right side ( SVW-2) is open and other solenoid valves are closed.
  • the solenoid valve (SVW-1) that opens to 2) and the secondary heat source heat exchanger (IB) located on the right side is opened, and the other solenoid valves are closed.
  • the two states are alternately switched.
  • the open / close state of the solenoid valves (SV7, SV8) provided on the first connection pipe (3A-1) and the second connection pipe (3A-2) depends on the indoor heat exchanger (3) that operates in cooling. Open the solenoid valve (SV7) of the first connection pipe (3A-1) and close the solenoid valve (SV8) of the second connection pipe (3A-2). On the other hand, the solenoid valve (SV8) of the second connection pipe (3A-2) connected to the indoor heat exchanger (3) for heating operation is opened and the solenoid valve (SV7) of the first connection pipe (3A-1) is opened. ) Is closed.
  • the liquid refrigerant power is supplied from the liquid pipe (7) to the indoor heat exchanger (3) that performs the cooling operation.
  • the liquid refrigerant is supplied from the second gas pipe (6B) through the second connection pipe (3A-2) to the indoor heat exchanger (3) for heating operation.
  • each indoor heat exchanger (3, 3,-) performs cooling operation and heating operation individually.
  • the primary-side refrigerant circuit (B) of the present embodiment is a modified example of the primary-side refrigerant circuit (A) combined with the secondary-side refrigerant circuit (B) of the above-described first embodiment, and includes a heat pump circuit. It is composed.
  • the primary-side refrigerant circuit (A) of this embodiment includes a compressor (11), a four-way switching valve (22), an outdoor heat exchanger (14), and a first electric valve (EVW).
  • a compressor 11
  • a four-way switching valve 22
  • an outdoor heat exchanger 14
  • a first electric valve EVW
  • a bypass line (BPL) that bypasses the auxiliary heat exchanger C15A) is provided between the primary heat source heat exchanger C12A) and the four-way switching valve (22).
  • the middle of this bypass line (BPL) is branched into two systems, one of which is a compressor
  • a check valve (CV-B1) and a discharge side solenoid valve (SV-B1) that allow only refrigerant flow from (11) to the primary heat source heat exchanger (12A) are provided.
  • the other branch pipe has a check valve (CV-B2) that allows only refrigerant to flow from the primary heat source heat exchanger (12A) to the compressor (11).
  • a suction-side solenoid valve (SV-B2) is provided.
  • the primary refrigerant circuit (A) is connected to the outdoor heat exchanger (14) to the discharge side of the force compressor (11) with the primary heat source heat exchange with the switching operation of the four-way switching valve (22).
  • the compressor (12A) is connected to the suction side of the compressor (11), respectively (the state shown by the solid line in Fig. 1), and the outdoor heat exchanger (14) is connected to the suction side of the compressor (11).
  • the state is switched to the state in which the side heat source heat exchanger (12A) is connected to the discharge side of the compressor (11) (the state shown by the broken line in Fig. 1).
  • the secondary refrigerant circuit (B) has the same configuration as that of the first embodiment described above.
  • Each solenoid valve (SV1.SV2, SV-B1.SV-B2), motor-operated valve (EVI, 13, EV1) and four-way switching valve (22) are opened and closed by the controller (C).
  • the indoor cooling operation of the refrigerant circuit (A, B) configured as described above will be described.
  • the primary-side refrigerant circuit (A) switches the four-way switching valve (22) to the solid line side, and adjusts the first electric valve (EVW) to a predetermined opening degree. Close the electrically operated valve (13) fully.
  • the bypass line (BPL) opens the intake solenoid valve (SV-B2) and closes the discharge solenoid valve (SV-B1).
  • the secondary refrigerant circuit (B) opens the first solenoid valve (SV1) and closes the second solenoid valve (SV2).
  • the secondary refrigerant circuit (B) As shown by the dashed-dotted arrow in Fig. 19, the secondary heat lost heat by exchanging heat with the primary heat source heat exchanger (12A).
  • the refrigerant in the side heat source heat exchanger (1) condenses, and the internal pressure in the secondary side heat source heat exchanger (1) decreases. Due to the pressure difference between the secondary-side heat source heat exchanger (1) and the indoor heat exchanger (3), the gas refrigerant in the indoor heat exchanger (3) passes through the gas pipe (6) to the secondary side. Collected in the heat source heat exchanger (1).
  • the gas refrigerant recovered in the source heat exchanger (1) is cooled by the coolant flowing through the primary heat source heat exchanger (12A) to become a liquid refrigerant, and stored in the secondary heat source heat exchanger (1). I do. After such an operation, a switching operation is performed in each of the refrigerant circuits (A, B), the first electric valve (EVW) is fully opened, and the second electric valve (13) is adjusted to a predetermined opening.
  • the bypass line (BPL) closes each solenoid valve (SV-B1, SV-B2).
  • the secondary refrigerant circuit (B) closes the first solenoid valve (SV1) and opens the second solenoid valve (SV2) and the indoor electric expansion valve (EV1).
  • the primary-side refrigerant circuit (A) As a result, in the primary-side refrigerant circuit (A), as shown by the dashed arrow in FIG. 19, the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is separated from the outside air in the outdoor heat exchanger (14). After being condensed by heat exchange, heat is exchanged with the secondary heat source heat exchanger (1) in the primary heat source heat exchanger (12A), and the refrigerant in the secondary heat source heat exchanger (1) After applying heat to the supercooled state, the pressure is reduced by the second motor-operated valve (13), the heat is exchanged with the outside air in the auxiliary heat exchanger (15A), and the refrigerant returns to the compressor (11) . This circulation operation is repeated.
  • the secondary-side refrigerant circuit (B) heat was given to the primary-side heat source heat exchanger (12A) by heat exchange as shown by the two-dot chain line arrow in Fig. 19. Part of the refrigerant in the secondary heat source heat exchanger (1) evaporates, and the internal pressure of the secondary heat source heat exchanger (1) increases. Due to the pressure difference between the secondary side heat source heat exchanger (1) and the indoor heat exchanger (3), the liquid refrigerant in the secondary side heat source heat exchanger (1) causes the liquid refrigerant in the secondary side heat source heat exchanger ( It is pushed out from the lower part of 1) to the indoor heat exchanger (3) via the liquid pipe (7). The liquid refrigerant extruded into the indoor heat exchanger (3) is decompressed by the indoor electric expansion valve (EV1), exchanges heat with the indoor air in the indoor heat exchanger (3), evaporates, and evaporates. To cool.
  • EV1 indoor electric expansion valve
  • each of the refrigerant circuits (A, B) as described above is performed alternately, so that the refrigerant circulates in the secondary refrigerant circuit (B) and cools the room.
  • heat transfer can be performed in the secondary-side refrigerant circuit (B) without providing a drive source such as a pump in the secondary-side refrigerant circuit (B).
  • the heating operation will be described with reference to FIG.
  • the primary side refrigerant circuit (A) moves the four-way switching valve (22) Side, the first motor-operated valve (EVW) is fully opened, and the second motor-operated valve (13) is adjusted to a predetermined opening.
  • the bypass line (BPL) closes each solenoid valve (SV-B1, SV-B2).
  • the secondary refrigerant circuit (B) closes the first solenoid valve (SV1) and opens the second solenoid valve (SV2).
  • the primary refrigerant circuit (A) the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is discharged to the outside air in the auxiliary heat exchanger (15A) as indicated by the solid arrow in FIG.
  • the pressure is reduced in the second motor-operated valve (13), and heat exchanges with the secondary heat source heat exchanger (1) in the primary heat source heat exchanger (12A) to evaporate Then, it returns to the compressor (11) via the outdoor heat exchanger (14). This circulation operation is repeated.
  • the secondary-side heat is removed from the primary-side heat source heat exchanger (12) and heat is taken away.
  • the refrigerant in the heat source heat exchanger (1) condenses, and the internal pressure of the secondary heat source heat exchanger (1) decreases. Due to the pressure difference between the secondary-side heat source heat exchanger (1) and the indoor heat exchanger (3), the liquid refrigerant of the indoor heat exchanger (3) passes through the liquid pipe (7) to the secondary-side heat source heat exchanger. Collected in exchanger (1).
  • a switching operation is performed in each of the refrigerant circuits (A, B), the first electric valve (EVW) is adjusted to a predetermined opening, and the second electric valve (13) is fully closed. I do.
  • the bypass line (BPL) the discharge side solenoid valve (SV-B1) is opened and the suction side solenoid valve (SV-B2) is closed.
  • the secondary refrigerant circuit (B) opens the first solenoid valve (SV1) and closes the second solenoid valve (SV2).
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) passes through the bypass line (BPL) and exchanges heat with the primary-side heat source.
  • the pressure is reduced in the first motor-operated valve (EVW) and evaporated in the outdoor heat exchanger (14). Return to (11). This circulation operation is repeated.
  • the secondary-side heat is exchanged with the primary-side heat source heat exchanger (12A) to give heat.
  • the refrigerant in the side heat source heat exchanger (1) evaporates, and the internal pressure of the secondary side heat source heat exchanger (1) rises. Due to the pressure difference between the secondary heat source heat exchanger (1) and the indoor heat exchanger (3), the gas refrigerant in the secondary heat source heat exchanger (1) converts the gas refrigerant in the secondary heat source heat exchanger (1).
  • the gas refrigerant supplied to the indoor heat exchanger (3) exchanges heat with the indoor air in the indoor heat exchanger (3), condenses and heats the indoor air.
  • each of the refrigerant circuits (A, B) as described above is performed alternately, so that the refrigerant circulates in the secondary refrigerant circuit (B) and heats the room. That is, even during this heating cultivation, heat transfer can be performed in the secondary-side refrigerant circuit (B) without providing a drive source such as a pump in the secondary-side refrigerant circuit (B).
  • the liquid refrigerant condensed in the outdoor heat exchanger (14) is cooled to a supercooled state in the primary heat source heat exchanger (12A). Therefore, the efficiency of the primary refrigerant circuit (A) can be improved.
  • FIG. 21 is a modification of the primary-side refrigerant circuit (A) combined with the secondary-side refrigerant circuit (B) of the tenth embodiment described above, and is an air conditioner that can switch between a cooling operation and a heating operation. Applied to the device.
  • the primary refrigerant circuit (A) of the present embodiment includes a compressor (11), first and second two-way switching valves (22A, 22B), an outdoor heat exchanger (14), and an electric valve ( EVW), the primary-side first heat source heat exchanger (12A-1), and the primary-side second heat source heat exchanger (12A-2) are connected by refrigerant piping (16).
  • the primary-side refrigerant circuit (A) was connected to the discharge side of the outdoor heat exchanger (14) and the force compressor (11) in accordance with the switching operation of the first four-way switching valve (22A).
  • the state is switched between the state (shown by the solid line in Fig. 21) and the state where the outdoor heat exchanger (14) is connected to the suction side of the compressor (11) (the state shown by the broken line in Fig. 21). .
  • the primary first heat source heat exchanger (12A-1) is connected to the outdoor heat exchanger in accordance with the switching operation of the second four-way switching valve (22B).
  • (14) shows the state in which the primary-side second heat source heat exchanger (12A-2) is connected to the compressor (11), respectively (the state shown by the solid line in Fig. 21).
  • the exchanger (12A-1) is supplied to the compressor (11), and the primary secondary heat source heat The state is switched to the state in which the exchanger (12A-2) is connected to the outdoor heat exchanger (14) (the state shown by the broken line in Fig. 21).
  • the secondary-side refrigerant circuit (B) is the same as that of the above-described tenth embodiment, and the secondary-side heat source heat exchanger (1A) located on the left side in FIG.
  • the secondary heat source heat exchanger (IB) located on the right side exchanges heat with the heat exchanger (12A-1) and the secondary heat source heat exchanger (12A-2), respectively.
  • the primary side refrigerant circuit (A) switches both the first four-way switching valve (22A) and the second four-way switching valve (22B) to the solid line side, and the motorized valve (EVW) is adjusted to the specified opening.
  • the secondary-side refrigerant circuit (B) has a solenoid valve (SVC-1) arranged in the secondary-side heat source heat exchanger (IB) located on the right side, and a secondary-side heat source heat exchanger (1A) located on the left side. Open the solenoid valve (SVC -2) connected to) and close other solenoid valves.
  • the secondary heat source heat exchanger IB) located on the right side is in a heat radiation state, and the indoor heat exchanger From (3), recover gas refrigerant from gas pipe (6).
  • the first secondary heat source heat exchanger (la) of the secondary heat source heat exchanger (1A) located on the left side becomes an endothermic state, and the internal pressure increases due to the evaporation of the refrigerant.
  • the liquid refrigerant is supplied from the liquid pipe (7) to the second indoor heat exchanger (3).
  • each refrigerant circuit (A, B) is switched. That is, The primary refrigerant circuit (A) switches the second four-way switching valve (22B) to the broken line side.
  • the secondary refrigerant circuit (B) has a solenoid valve (SVC-2) connected to the secondary heat source heat exchanger (IB) located on the right side, and a secondary heat source heat exchanger (1A) located on the left side. Open the solenoid valve (SVC-1) and close other solenoid valves.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) flows into the outdoor heat exchanger (14) as indicated by the dashed line in FIG. Then, heat exchanges with the outside air and condenses, and heat exchanges with one of the secondary heat source heat exchangers (1B) in the secondary heat source heat exchanger (12A-2) on the primary side. Heat is given to the refrigerant in the heat source heat exchanger (1B), resulting in a supercooled state.
  • the liquid refrigerant is decompressed by the motor-operated valve (EVW) and heat exchanges with the other secondary heat source heat exchanger (1A) in the primary heat source heat exchanger (12A-1) on the primary side. After removing heat from the refrigerant in the secondary heat source heat exchanger (1A) and evaporating, the refrigerant returns to the compressor (11). This circulation operation is repeated.
  • EVW motor-operated valve
  • the secondary-side heat source heat exchanger (1A) located on the left side is in a radiating state, and the liquid refrigerant is recovered from the indoor heat exchanger (3).
  • the first secondary-side heat source heat exchanger (la) of the secondary-side heat source heat exchanger (1B) located on the right side becomes an endothermic state, and the second internal-side heat source heat exchanger (la) increases with the internal pressure due to the evaporation of the refrigerant.
  • the secondary heat source heat exchanger (lb) supplies liquid refrigerant to the indoor heat exchanger (3).
  • the heat-dissipating state and the heat-absorbing state of the two secondary-side heat source heat exchangers (1A, 1B) are alternately repeated. As a result, the room is continuously cooled, and the air conditioning performance can be improved.
  • the indoor heating operation of the refrigerant circuit (A, B) configured as described above will be described.
  • the primary side refrigerant circuit (A) moves the first four-way switching valve (22A) to the broken line side and the second four-way switching valve (22B) to the solid line side. Switch each and adjust the electric valve (EVW) to the specified opening.
  • the secondary refrigerant circuit (B) is connected to the solenoid valve (SVI-1) to the secondary heat source heat exchanger (IB) on the right side and the secondary heat source heat exchanger C1A to the left. Open the solenoid valve (SVW-2) and close other solenoid valves.
  • the primary-side refrigerant circuit (A) is as shown in Fig. 22.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) is connected to one secondary-side heat source heat exchanger (IB) in the primary-side second heat source heat exchanger C12A-2). Heat exchanges between and condenses.
  • the liquid refrigerant is depressurized by the electric valve (EVW) and exchanges heat with the other secondary heat source heat exchanger (U) in the primary first heat source heat exchanger (12A-1). It evaporates and returns to the compressor (11) via the outdoor heat exchanger (14). This circulation operation is repeated.
  • the secondary-side heat source heat exchanger (1A) located on the left side is in a heat-release state, and recovers the liquid refrigerant from the indoor heat exchanger (3).
  • the secondary heat source heat exchanger (IB) located on the right side absorbs heat and supplies gas refrigerant to the indoor heat exchanger (3) as the internal pressure rises due to evaporation of the refrigerant.
  • each refrigerant circuit (A, B) is switched. That is, the primary-side refrigerant circuit (A) switches the second four-way switching valve (22B) to the broken line side.
  • the secondary refrigerant circuit (B) has a solenoid valve (SVW-2) connected to the secondary heat source heat exchanger (IB) located on the right side, and a secondary heat source heat exchanger (1A) located on the left side. Open the solenoid valve (SVW-1) connected to, and close other solenoid valves.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor (11) flows into the primary-side first heat source heat exchanger as indicated by the dashed line arrow in FIG.
  • the vessel (12A-1) heat exchanges with one of the secondary heat source heat exchangers (U) to condense.
  • the liquid refrigerant is depressurized by the electric valve (EVW) and exchanges heat with the other secondary heat source heat exchanger (IB) in the primary secondary heat source heat exchanger (12A-2). Evaporates and returns to the compressor (11) via the outdoor heat exchanger (14). This circulation operation is repeated.
  • the secondary-side heat source heat exchanger (1A) located on the left side absorbs heat, and the indoor heat exchanger (3) Supply liquid refrigerant to the line.
  • the first secondary heat source heat exchanger (la) of the secondary heat source heat exchanger (1B) located on the right side is in a strong heat radiation state, and the liquid refrigerant is discharged from the indoor heat exchanger (3). to recover.
  • the heat-dissipating state and the heat-absorbing state of the two secondary-side heat source heat exchangers (1A, IB) are alternately repeated. As a result, the room is continuously cooled, and the air conditioning performance can be improved.
  • the force described when the heat transfer device according to the present invention is applied to a refrigerant circuit of an air conditioner ⁇ The present invention is not limited to this, and can be applied to various other refrigerators. .
  • the present invention is useful for a heat transfer device that can be used as a refrigerant circuit or the like of an air conditioner, and in particular, circulates a heat transfer medium without requiring a drive source such as a pump. It is suitable for a heat transfer device that transfers heat.

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Abstract

Un échangeur de chaleur (1) monté sur une source de chaleur secondaire, échange de la chaleur avec un échangeur de chaleur (12) monté sur la source de chaleur primaire d'un circuit de refroidissement primaire (A). Ce circuit de refroidissement (A) est raccordé à un échangeur de chaleur d'intérieur (3) par un tuyau à gaz (6) et un tuyau à liquides (7) équipés de leurs électrovannes respectives (SV1, SV2). Pendant la diffusion de chaleur par l'échangeur de chaleur (12) du côté du primaire, l'électrovanne (SV2) du tuyau pour liquide (7) est la seule à être ouverte. La haute pression de vapeur du fluide de refroidissement évaporé par l'échangeur de chaleur (1) chasse alors le liquide de refroidissement de l'échangeur de chaleur (1) du côté du secondaire vers l'échangeur de chaleur d'intérieur (3). Pendant l'absorption de chaleur par l'échangeur de chaleur (12), l'électrovanne (SV1) du tuyau pour gaz (6) est la seule à être ouverte. La basse pression de vapeur du fluide de refroidissement condensé par l'échangeur de chaleur (1) aspire alors le fluide de refroidissement gazeux de l'échangeur de chaleur d'intérieur (3) vers l'échangeur de chaleur (1).
PCT/JP1996/003130 1995-10-24 1996-10-24 Systeme de transport de chaleur WO1997015800A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP96935453A EP0857937B1 (fr) 1995-10-24 1996-10-24 Systeme de transport de chaleur
DE69618474T DE69618474T2 (de) 1995-10-24 1996-10-24 Wärmetransportsystem
AU73369/96A AU717801B2 (en) 1995-10-24 1996-10-24 Heat transport system
US09/051,484 US5943879A (en) 1995-10-24 1996-10-24 Heat transport system
HK99102449A HK1017423A1 (en) 1995-10-24 1999-06-02 Heat transfer apparatus

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP7/275642 1995-10-24
JP27564295A JP3582185B2 (ja) 1995-10-24 1995-10-24 熱搬送装置

Publications (1)

Publication Number Publication Date
WO1997015800A1 true WO1997015800A1 (fr) 1997-05-01

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PCT/JP1996/003130 WO1997015800A1 (fr) 1995-10-24 1996-10-24 Systeme de transport de chaleur

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US (1) US5943879A (fr)
EP (1) EP0857937B1 (fr)
JP (1) JP3582185B2 (fr)
KR (1) KR100399272B1 (fr)
CN (1) CN1110683C (fr)
AU (1) AU717801B2 (fr)
DE (1) DE69618474T2 (fr)
ES (1) ES2170877T3 (fr)
HK (1) HK1017423A1 (fr)
WO (1) WO1997015800A1 (fr)

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EP0857937A4 (fr) 2000-07-26
CN1110683C (zh) 2003-06-04
CN1200802A (zh) 1998-12-02
DE69618474D1 (de) 2002-02-14
AU717801B2 (en) 2000-03-30
JPH09119735A (ja) 1997-05-06
KR100399272B1 (ko) 2004-02-18
HK1017423A1 (en) 1999-11-19
KR19990067025A (ko) 1999-08-16
JP3582185B2 (ja) 2004-10-27
EP0857937B1 (fr) 2002-01-09
US5943879A (en) 1999-08-31
DE69618474T2 (de) 2002-06-06
ES2170877T3 (es) 2002-08-16
EP0857937A1 (fr) 1998-08-12
AU7336996A (en) 1997-05-15

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